US4774852A - Campshaft for actuating valve tappets in internal combustion engines - Google Patents

Campshaft for actuating valve tappets in internal combustion engines Download PDF

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Publication number
US4774852A
US4774852A US07/008,309 US830987A US4774852A US 4774852 A US4774852 A US 4774852A US 830987 A US830987 A US 830987A US 4774852 A US4774852 A US 4774852A
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US
United States
Prior art keywords
shaft
cam member
projection
cam
strip
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
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US07/008,309
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English (en)
Inventor
Lukas Matt
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Supervis
Original Assignee
Supervis
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Assigned to ETABLISSEMENT SUPERVIS, ALTENBACHSTRASSE 17, FL-9490 VADUZ, LIECHTENSTEIN reassignment ETABLISSEMENT SUPERVIS, ALTENBACHSTRASSE 17, FL-9490 VADUZ, LIECHTENSTEIN ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: MATT, LUKAS
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H53/00—Cams or cam-followers, e.g. rollers for gearing mechanisms
    • F16H53/02—Single-track cams for single-revolution cycles; Camshafts with such cams
    • F16H53/025—Single-track cams for single-revolution cycles; Camshafts with such cams characterised by their construction, e.g. assembling or manufacturing features
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
    • F16D1/08—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key
    • F16D1/0829—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial loading of both hub and shaft by an intermediate ring or sleeve
    • F16D1/0835—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial loading of both hub and shaft by an intermediate ring or sleeve due to the elasticity of the ring or sleeve
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T403/00—Joints and connections
    • Y10T403/70—Interfitted members
    • Y10T403/7047—Radially interposed shim or bushing
    • Y10T403/7061—Resilient
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2101—Cams

Definitions

  • the present invention relates to a camshaft for actuating valve tappets in internal combustion engines.
  • the camshaft includes a shaft member and at least one cam member slid onto and connected to the shaft member.
  • the cam member defines an axial bore having a shape which essentially corresponds to the cross-sectional profile of the shaft member.
  • Camshafts of internal combustion engines are highly stressed structural machine parts.
  • the large number of prior art publications in this area make it clear that substantial efforts have been made to find economical and technically satisfactory solutions for manufacturing useful camshafts.
  • camshafts are known in which the cams and the shaft are manufactured separately and are subsequently joined together to form a structural unit.
  • the shaft is provided with a plurality of axially extending grooves and the bore in the cam has a corresponding radial projection which engages into one of these grooves.
  • the bore of the cam surrounds the shaft with play and the aforementioned projection has such a size in radial direction that cam and shaft can be joined together and are locked together by means of a frictional engagement.
  • the gap resulting from the aforementioned play is being filled with brazing solder from the outside after cam and shaft have been joined together.
  • the number of grooves provided circumferentially on the shaft corresponds to the cam phase relationship required for the respective purpose of the camshaft. This construction is not advantageous because it is very difficult to manufacture the grooves on the shaft in exactly the correct position. These grooves must be manufactured very precisely, i.e., they must be exactly positioned with respect to their angular location.
  • U.S. Pat. No. 3,543,589 shows and describes a cam disk with balanced, spring-loaded feeler rollers.
  • the cam disk has a plurality of essentially equal cam pumps which are uniformly distributed around an axis.
  • two spaced-apart distance rollers are provided in such a manner relative to the cam disk that, when one feeler roller is on an ascending portion of a cam hump and, thus, removes energy from the drive mechanism, the other feeler roller rolls on a descending portion of a cam hump and, thus, returns energy into the system, wherein the energy returned is the same as that being removed from the system by the first feeler roller.
  • the drawings of this patent illustrate this concept.
  • the drawings also show the construction of the cam disk or control switch.
  • a cam disk having an even number or an odd number of cam humps is arranged on a shaft of circular cross-section.
  • the shaft is not indicated in detail.
  • the feeler rollers are supported by resilient plates which, in turn, have electrical contacts, the feeler rollers are located relative to the cam disk in such a way that, when the cam disk is rotating, one of the feeler rollers rolls upwardly on a cam hump, while the other feeler roller simultaneously rolls down such a cam hump.
  • the connection between the drive shaft and cam disk is formed by a hollow cylindrical element which is made of a macromolecular material.
  • the cam disk for controlling the feeler rollers or the switching springs can only handle small loads.
  • the cam disk is to be uniformly stressed during a full rotation.
  • the principal concept on which the prior aforedescribed construction is based is the energy recuperation and the resulting reduction of the torque of the drive motor.
  • This tolerance ring is an undulated spring steel strip which is bent into an open ring having a longitudinal slot. This ring is either slid onto the shaft or inserted into the hub bore. The size of the ring is such that, when the ring is inserted, the edges defining the longitudinal slot are spaced apart from each other.
  • tolerance rings have been found very useful in general mechanical engineering because they facilitate a quick, inexpensive assembly and a simple construction of parts to be connected.
  • the rings can compensate to a high degree different thermal expansions between machine elements of the different materials.
  • the rings are resistant to temperature changes, they permit great tolerances between parts to be connected and, moreover, they are resistant to chemical attack.
  • a camshaft is a machine element of a special type, especially because during normal operation, it is subjected to very extreme dynamic loads.
  • all cam shafts have a connection between shaft and cam which is an integrally formed material connection and/or a positively locked connection.
  • the primary object of the present invention to simplify the manufacture of such a camshaft and, simultaneously, to improve its quality, while the shaft and the cams are still connected to each other only by frictional engagement and structural elements are used which are known for such a connection.
  • this complex object is met by providing between cam and shaft an undulated spring steel strip or tolerance ring which has a longitudinal slot, wherein the edges defining the longitudinal slot are braced in circumferential direction of the spring steel strip when the spring steel strip is placed in the bore of the cam or is slid onto the shaft in an unloaded state, i.e., prior to putting together the parts to be joined.
  • FIG. 1 is a perspective view of a portion of a camshaft
  • FIG. 2 is a side view of the cam of the camshaft of FIG. 1, on a larger scale;
  • FIG. 3 is a cross-sectional view of the camshaft of FIG. 1, also on a larger scale;
  • FIG. 4 shows a detail from FIG. 3 within circle A, on an even larger scale
  • FIG. 5 is a diagram showing the pattern of the radial force acting on the cam during a rotation of the camshaft
  • a camshaft illustrated in FIG. 1 includes a shaft 1 formed by a pipe and cams 2 mounted on the shaft 1.
  • the cams 2 are spaced apart from each other in axial direction of the shaft 1.
  • the cams are angularly offset relative to each other as it corresponds to the respective phase relationship of the motor elements to be actuated by the cam shaft.
  • FIG. 2 is an elevational view of a cam on a larger scale as compared to FIG. 1.
  • the cam or its outer contour is symmetrical with respect to the axis 10.
  • Cam 2 has a bore 3 whose diameter is slightly greater than the outer diameter of shaft 1.
  • the surface formed by bore 3 has a projection 8 which protrudes toward the center of the cam.
  • the projection 8 is defined by two essentially radially extending sides 4 and a surface 5 of the projection 8 facing the shaft 1 is formed as a partial cylindrical surface whose curvature essentially corresponds to the curvature of shaft 1.
  • surface 5 rests completely without play on shaft 1 after the cam 2 has been mounted on the shaft.
  • the offsetting between cam 2 and shaft 1 is extremely small during assembly.
  • a slotted, undulated spring steel strip 6 is placed between shaft 1 and the wall of bore 3.
  • Strip 6 has a radial thickness s which corresponds to half the difference of the diameter of the bore 3 and the outer diameter of shaft 1.
  • the radially measured height of projection 8 also corresponds approximately to this dimension s.
  • Spring steel strips 6 of the above-mentioned type are known. They are called tolerance rings and are part of the group of connecting elements which are generally called tension springs.
  • This tolerance ring is such that the edges 7 which define its longitudinal slot rests against the sides of projection 8 when the ring is properly inserted and unstressed, as illustrated in FIG. 4.
  • Tolerance ring 6 is called unstressed in this connection when it is placed in bore 3 of cam 2 with the cam 2 not yet being slid onto shaft 1, while the edges 7 of the longitudinal slots are already resting against the sides 4 of projection 8.
  • projection 8 is provided in that angular area which corresponds to the angle ⁇ E shown in the diagram of FIG. 5.
  • each cam 2 is braced relative to shaft 1 at the moment of its highest radial stress by means of the aforementioned surface 5 of projection 8.
  • cam 2 is braced relative to shaft 1 through tolerance ring 6 which provides an extremely safe and secure support of cam 2 on shaft 1 due to the circumferential clamping resulting from the bracing of the edges 7 of the longitudinal slot against the sides 4 of projection 8.
  • German Offenlegungsschrift No. 33 21 846 in which a triangle-shaped cam in a hub is offset by an angle ⁇ relative to the plane of symmetry of this cam.
  • This angle ⁇ is equal to half the angle ⁇ which, in turn, corresponds to the angle between inlet and outlet valve.
  • the claimed angle position is a function of the cam.
  • forces can be transmitted in circumferential direction only by the spring and groove connection provided in that case.
  • the springs are angularly offset, so that only every other cam along the camshaft has its spring projection at the correct place, wherein the spring projections shown in German Offenleungsschrift No. 33 21 846 have the sole purpose of positioning.
  • the cam can assume any angular position relative to the shaft.
  • a plurality of angularly offset cams 2 are placed on shaft 1.
  • the camshaft is assembled by placing the tolerance rings into the bores 3 of the cams and sliding the cams prepared in this manner onto the shaft 1 in the appropriate angular position relative to the shaft. Extensive tests have shown that the tolerance ring 6 braced in this manner provides a safe and secure connection, even when the camshaft is sub-jected to very high stress.
  • the tool used for assembling the camshaft is constructed in such a way that it ensures that the tolerance ring 6 maintains its correct position within bore 3 during the sliding of the cam 2 onto the shaft 1.
  • the camshaft When the camshaft is assembled, the cams are placed in a tool with the appropriate axial spacing and offset as intended.
  • the support members for the cam in this tool may be connected to load measuring devices, so that, when the shaft 1 is inserted, it can be determined whether the connecting force required for a proper and safe seat of the shaft has been reached.
  • the cam 2 may be made of a solid material in a chip-removing method. However, it advantageous to sinter the cam, i.e., to use a manufacturing process which is particularly advantageous if the cylinder wall of bore 3 for receiving the shaft 1 is interrupted by projection 8.
  • the projection 8 against whose sides 4 the edges 7 of the longitudinal slot of the tolerance ring 6 are braced is formed integrally with the cam 2.
  • a ledge of the described type could be manufactured as a separate structural component and could be inserted between shaft 1 and cam 2 together with tolerance ring 6.
  • Such a ledge could have a height which is greater than half the difference of the inner diameter of the bore 3 and the outer diameter of shaft 1.
  • a groove would have to be provided in the shaft and/or in the cam which groove receives a portion of the height of such a ledge during the assembly.
  • the shaft 1 may be a cold drawn pipe which does not have to be finished.
  • the proposal according to the present invention is distinguished by a particularly simple structure which can be reached simply and inexpensively.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Gears, Cams (AREA)
US07/008,309 1986-02-26 1987-01-29 Campshaft for actuating valve tappets in internal combustion engines Expired - Lifetime US4774852A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3606111 1986-02-26
DE19863606111 DE3606111A1 (de) 1986-02-26 1986-02-26 Nockenwelle

Publications (1)

Publication Number Publication Date
US4774852A true US4774852A (en) 1988-10-04

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US07/008,309 Expired - Lifetime US4774852A (en) 1986-02-26 1987-01-29 Campshaft for actuating valve tappets in internal combustion engines

Country Status (4)

Country Link
US (1) US4774852A (enrdf_load_stackoverflow)
EP (1) EP0234398B1 (enrdf_load_stackoverflow)
JP (1) JPS62199908A (enrdf_load_stackoverflow)
DE (1) DE3606111A1 (enrdf_load_stackoverflow)

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4947547A (en) * 1987-05-22 1990-08-14 Etablissement Supervis Method of manufacturing a camshaft
US5197351A (en) * 1989-02-28 1993-03-30 Viv Engineering Inc. Cam shaft and process for manufacturing the same
US5205187A (en) * 1987-05-12 1993-04-27 Gesenkschmiede Schneider Gmbh Hollow shaft
US5307708A (en) * 1991-07-03 1994-05-03 Etablissement Supervis Camshaft for controlling valves in internal combustion engines
US5337626A (en) * 1993-02-23 1994-08-16 Ryobi Outdoor Products, Inc. Laminated gear and method of forming a laminated gear
US5357067A (en) * 1993-05-18 1994-10-18 Dwyer Instruments, Inc. Cam arrangement for use in rotary position indicators
US5738052A (en) * 1995-06-02 1998-04-14 Ford Global Technologies, Inc. Composite camshaft for internal combustion engine
US6189194B1 (en) * 1996-06-26 2001-02-20 Daimlerchrysler Ag Method for joining and inspecting
US20060046858A1 (en) * 2004-08-26 2006-03-02 Ronald Brissette Driveshaft assembly with torque ring coupling
US20060110211A1 (en) * 2003-02-11 2006-05-25 Carman Gregory P Infinitely adjustable engagement system and method
US20100038167A1 (en) * 2007-04-19 2010-02-18 Thyssenkrupp Presta Aktiengesellschaft Toothed rack or threaded rod
US20100052280A1 (en) * 2007-04-19 2010-03-04 Thyssenkrupp Presta Aktiengesellschaft Toothed rack or threaded rod
US20130125699A1 (en) * 2010-07-29 2013-05-23 Neumayer Tekfor Holding Gmbh Method for the Manufacture of a Camshaft
US20130220068A1 (en) * 2010-10-12 2013-08-29 Neumayer Tekfor Holding Gmbh Method for Producing a Functional Shaft
US20150114170A1 (en) * 2012-06-01 2015-04-30 Schaeffler Technologies Gmbh & Co. Kg Main shaft for a sliding cam valve train
CN111279090A (zh) * 2017-09-29 2020-06-12 圣戈班性能塑料万科有限公司 公差环

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3606111A1 (de) * 1986-02-26 1987-08-27 Supervis Ets Nockenwelle
US4809562A (en) * 1987-09-30 1989-03-07 The Torrington Company Camshaft manufacture
DE19716320C2 (de) * 1997-04-18 1999-04-29 Bauss Hans Werner Nockenwelle
JP4671465B2 (ja) * 1999-04-27 2011-04-20 幸義 村上 孔を有する部材に嵌合する中空シャフト部材
EP1409891B1 (de) * 2001-07-20 2006-05-03 ThyssenKrupp Presta AG Nocken mit aufnahmeöffnugen für eine welle und verfahren zur herstellung einer nockenwelle mit diesen nocken
DE10260115B4 (de) * 2002-12-19 2005-01-27 Thyssenkrupp Automotive Ag Nockenwelle aus Kohlenfaserverbundwerkstoff (CFK)
DE102009051636A1 (de) 2009-11-02 2011-05-05 Thyssenkrupp Presta Teccenter Ag Verfahren zur Herstellung eines Nockenwellenmoduls, Nockenwellenmodul sowie gebauten Nockenwelle
DE102011001543B4 (de) * 2011-03-24 2015-09-03 Thyssenkrupp Presta Teccenter Ag Nockenwelle in Leichtbauweise
DE102013211936A1 (de) * 2013-06-24 2014-12-24 Mahle International Gmbh Welle-Nabe-Verbindung

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GB189719932A (en) * 1897-08-30 1898-01-01 Edwin Taylor Improvements in the Mode and Means for Making the Junctions of Cycle, Motor Car and other Frames, Bedstead and Fender Junctions, and other Purposes.
US1390949A (en) * 1921-03-21 1921-09-13 Universal Parts Company Cam-shaft and process of making the same
US1441484A (en) * 1921-01-17 1923-01-09 Jacob B Conover Milk and ice-cream can and method of making the same
GB223300A (en) * 1923-07-17 1924-10-17 Charles Herbert Apsey Improvements in joints or couplings for metal tubes, tubular framework, rods or othermetal articles
GB547988A (en) * 1940-11-12 1942-09-21 Tinnerman Products Inc Improvements relating to fastening means for securing handles, knobs and other articles to stems or the like
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US2886354A (en) * 1950-02-02 1959-05-12 Bjorklund Gustaf Erik Fasteners
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EP0234398A2 (de) * 1986-02-26 1987-09-02 Etablissement Supervis Nockenwelle zur Betätigung von Ventilstössel bei Verbrennungskraftmaschinen

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US1441484A (en) * 1921-01-17 1923-01-09 Jacob B Conover Milk and ice-cream can and method of making the same
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GB223300A (en) * 1923-07-17 1924-10-17 Charles Herbert Apsey Improvements in joints or couplings for metal tubes, tubular framework, rods or othermetal articles
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US2477995A (en) * 1945-04-28 1949-08-02 Belmont Radio Corp Shaft-positioning apparatus
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GB1073147A (en) * 1963-09-18 1967-06-21 Star Kugelhalter Gmbh Dt Improvements in and relating to connecting elements for interfitting parts
US3438660A (en) * 1964-10-23 1969-04-15 Lajos Steiner Mechanical clamping means
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DE2443318A1 (de) * 1973-09-11 1975-04-03 Nippon Piston Ring Co Ltd Gewelltes, radiales distanzspreizelement fuer zusammengesetzte oelabstreifringe
US3978945A (en) * 1974-09-17 1976-09-07 The B. F. Goodrich Company Brake disc mounting
US4068906A (en) * 1975-11-26 1978-01-17 Hydrel A.G. System for securing guide rails in machine stand
DE2657479A1 (de) * 1976-12-10 1978-06-15 Sulzer Ag Verfahren und vorrichtung zum befestigen eines nockens auf einer welle
DE2838995A1 (de) * 1977-09-08 1979-03-15 Toyota Motor Co Ltd Verfahren und vorrichtung zum herstellen und zusammenbauen einer nockenwelle
DE3321846A1 (de) * 1982-06-17 1983-12-22 Nippon Piston Ring Co., Ltd., Tokyo Nockenwelle fuer die verwendung in einer brennkraftmaschine
GB2121908A (en) * 1982-06-17 1984-01-04 Nippon Piston Ring Co Ltd A camshaft
US4569614A (en) * 1982-06-30 1986-02-11 Yukio Yamauchi Coupling
DE3409541A1 (de) * 1984-03-15 1985-11-07 Gesenkschmiede Schneider Gmbh, 7080 Aalen Hohlwelle zur uebertragung von drehmomenten
EP0234398A2 (de) * 1986-02-26 1987-09-02 Etablissement Supervis Nockenwelle zur Betätigung von Ventilstössel bei Verbrennungskraftmaschinen

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Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5205187A (en) * 1987-05-12 1993-04-27 Gesenkschmiede Schneider Gmbh Hollow shaft
US4947547A (en) * 1987-05-22 1990-08-14 Etablissement Supervis Method of manufacturing a camshaft
US5197351A (en) * 1989-02-28 1993-03-30 Viv Engineering Inc. Cam shaft and process for manufacturing the same
US5307708A (en) * 1991-07-03 1994-05-03 Etablissement Supervis Camshaft for controlling valves in internal combustion engines
US5337626A (en) * 1993-02-23 1994-08-16 Ryobi Outdoor Products, Inc. Laminated gear and method of forming a laminated gear
US5357067A (en) * 1993-05-18 1994-10-18 Dwyer Instruments, Inc. Cam arrangement for use in rotary position indicators
US5738052A (en) * 1995-06-02 1998-04-14 Ford Global Technologies, Inc. Composite camshaft for internal combustion engine
US6189194B1 (en) * 1996-06-26 2001-02-20 Daimlerchrysler Ag Method for joining and inspecting
US20060110211A1 (en) * 2003-02-11 2006-05-25 Carman Gregory P Infinitely adjustable engagement system and method
US20070105632A1 (en) * 2004-08-26 2007-05-10 Ronald Brissette Driveshaft assembly with torque ring coupling
US20060046858A1 (en) * 2004-08-26 2006-03-02 Ronald Brissette Driveshaft assembly with torque ring coupling
US20100038167A1 (en) * 2007-04-19 2010-02-18 Thyssenkrupp Presta Aktiengesellschaft Toothed rack or threaded rod
US20100052280A1 (en) * 2007-04-19 2010-03-04 Thyssenkrupp Presta Aktiengesellschaft Toothed rack or threaded rod
US7887069B2 (en) 2007-04-19 2011-02-15 Thyssenkrupp Presta Aktiengesellschaft Toothed rack or threaded rod
US20130125699A1 (en) * 2010-07-29 2013-05-23 Neumayer Tekfor Holding Gmbh Method for the Manufacture of a Camshaft
US20130220068A1 (en) * 2010-10-12 2013-08-29 Neumayer Tekfor Holding Gmbh Method for Producing a Functional Shaft
US9273770B2 (en) * 2010-10-12 2016-03-01 Neumayer Tekfor Holding Gmbh Method for producing a functional shaft
US10247225B2 (en) 2010-10-12 2019-04-02 Neumayer Tekfor Engineering Gmbh Device for producing a functional shaft
US20150114170A1 (en) * 2012-06-01 2015-04-30 Schaeffler Technologies Gmbh & Co. Kg Main shaft for a sliding cam valve train
CN111279090A (zh) * 2017-09-29 2020-06-12 圣戈班性能塑料万科有限公司 公差环
US11499591B2 (en) 2017-09-29 2022-11-15 Saint-Gobain Performance Plastics Rencol Limited Tolerance ring
US11859670B2 (en) 2017-09-29 2024-01-02 Saint-Gobain Performance Plastics Rencol Limited Tolerance ring

Also Published As

Publication number Publication date
EP0234398B1 (de) 1989-04-26
DE3606111C2 (enrdf_load_stackoverflow) 1992-09-03
JPS62199908A (ja) 1987-09-03
EP0234398A3 (en) 1987-10-21
DE3606111A1 (de) 1987-08-27
EP0234398A2 (de) 1987-09-02

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